EP0579869B1 - Führungshülse mit integrierter Dichtung für ein Kupplungsausrücklager eines Getriebes - Google Patents

Führungshülse mit integrierter Dichtung für ein Kupplungsausrücklager eines Getriebes Download PDF

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Publication number
EP0579869B1
EP0579869B1 EP92121544A EP92121544A EP0579869B1 EP 0579869 B1 EP0579869 B1 EP 0579869B1 EP 92121544 A EP92121544 A EP 92121544A EP 92121544 A EP92121544 A EP 92121544A EP 0579869 B1 EP0579869 B1 EP 0579869B1
Authority
EP
European Patent Office
Prior art keywords
sealing lip
axial
radial
guide bush
seal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92121544A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0579869A3 (enrdf_load_stackoverflow
EP0579869A2 (de
Inventor
Gerhard Freiwald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carl Freudenberg KG
Original Assignee
Carl Freudenberg KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carl Freudenberg KG filed Critical Carl Freudenberg KG
Publication of EP0579869A2 publication Critical patent/EP0579869A2/de
Publication of EP0579869A3 publication Critical patent/EP0579869A3/xx
Application granted granted Critical
Publication of EP0579869B1 publication Critical patent/EP0579869B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F16D23/148—Guide-sleeve receiving the clutch release bearing

Definitions

  • the invention relates to a guide sleeve with an integrated seal for the clutch release bearing of a transmission, comprising a pipe socket surrounding an input shaft of the transmission with a radial spacing on the circumference and a fastening flange fixed to the pipe socket, the pipe socket on the side facing the outer wall of the transmission having a substantially Z-shaped shape Cross section, wherein the Z-shaped cross section is formed by a radially inner first axial leg and a radially outer second axial leg and wherein the first and the second axial leg are connected to each other by a radial leg, the seal on the side facing the input shaft to be sealed is provided with at least one dynamically stressed first sealing lip and is fixed to a stiffening ring made of a non-creeping material and wherein the stiffening ring is held in the pipe socket under radial prestress is.
  • Such a guide sleeve is known from EP-A-0 336 843 A1.
  • the seal comprises a stiffening ring with a substantially T-shaped cross-section, the elastomeric material of the seal being fixed to the radial projection of the stiffening ring.
  • the stiffening ring In the axial direction, on the one hand, the stiffening ring is arranged under radial prestress within the second axial leg of the guide sleeve, the stiffening ring in the axial direction, on the other hand, being designed as a centering collar for centering the guide sleeve on a gearbox housing.
  • the seal has a dynamically stressed sealing lip, which is enclosed on the outside in the radial direction by an annular spiral spring is. At an axial distance adjacent to the dynamically stressed sealing lip, a further sealing lip is provided on the side facing away from the transmission in order to keep contaminants away from the dynamically stressed sealing lip.
  • Another guide sleeve is known from EP-A-0 301 965 A1.
  • the known guide sleeve for the clutch release bearing of a motor vehicle transmission shows a fastening flange for fastening the guide sleeve to the outer surface of a transmission housing wall, the fastening flange being arranged in the same radial plane as a pipe section which receives the sealing ring.
  • the sealing ring is arranged on a pipe section extending in the radial direction and thus relaxation phenomena of the elastomeric material are promoted, which can lead to leaks in the area of the dynamic seal.
  • the invention has for its object to effect an improved dynamic sealing of the input shaft by a more stable fixing of the seal within the pipe socket and at the same time to statically seal the outer wall of the transmission during a long period of use.
  • the seal has a Z-shaped profile which is adapted to the pipe socket and is statically stressed on the side facing the outer wall of the transmission with at least one axially protruding in the direction of the outer wall and can be brought into sealing engagement therewith second sealing lip is provided that the first and the second sealing lip are integrally fixed to each other on the stiffening ring and that the stiffening ring is held in the first axial leg.
  • the first and second sealing lips being integrally merged into one another on a Z-shaped stiffening ring made of a non-creeping material, for example metal, and this is under radial prestress from the first Axial leg of the pipe socket, which is preferably also made of a metallic material, is enclosed, there is a stable spatial assignment of the sealing lips in relation to the surfaces to be sealed and the pipe socket. It is also an advantage that in the case of radial deflection movements of the input shaft to be sealed, the seal on the stiffening ring is only loaded under pressure.
  • the stiffening ring can touch the radial leg and the axial preload.
  • the axial preload is generated by the fact that the statically stressed second sealing lip is elastically deformed when the guide sleeve is mounted on the end wall of the transmission, so that the stiffening ring, which is arranged on the side of the second sealing lip opposite the end wall, on the radial leg of the clutch guide sleeve is created.
  • the sealing lip may at least partially be completely covered by the second axial leg, the second axial leg appropriately touching the outer wall of the transmission in the region of its end face.
  • the second axial limb requires, on the one hand, protection of the second sealing lip from external influences and, on the other hand, protection of the second sealing lip from excessive pressure in the axial direction.
  • the assembly of the guide sleeve is considerably simplified in that it is screwed onto the outer wall of the gear unit until the end face of the second axial leg lies against the outer wall of the gear unit.
  • the second sealing lip protruding axially over the end face of the second axial leg before assembly then touches the outer wall of the transmission under a predetermined axial pressure.
  • the pipe socket and the fastening flange can be formed in one piece. In addition to being easier to manufacture due to fewer parts that have to be assembled, the assembly is simplified.
  • An improved static seal can be achieved in that the second sealing lip with a radially adjacent additional sealing lip delimits a gap which is provided with a grease filling.
  • a particularly stable and precise assignment of the seal within the pipe socket can be achieved in that the ratio of the axial expansion of the seal to the radial expansion is 1: 1 to 1: 0.25. Signs of tilting when the input shaft to be sealed is displaced are not to be feared by this configuration. Because the radial Expansion is at most as great as the axial expansion of the seal, but preferably significantly less, results in a particularly long guidance of the dynamically stressed first sealing lip within the radially inner first axial leg, so that manufacturing-related tolerances of the pipe socket do not have a negative influence on the properties of use the guide sleeve. A particularly high degree of dimensional accuracy of the first axial leg in relation to the radial leg is therefore not necessary, as a result of which the guide sleeve can be manufactured more simply and economically.
  • the dynamically stressed first sealing lip can be delimited by intersecting conical surfaces, the conical surface arranged on the side facing the medium to be sealed enclosing a larger angle with the longitudinal axis of the guide sleeve than the conical surface on the axially opposite side. This configuration brings about a return flow effect of the medium to be sealed in the direction of the space to be sealed and a constant renewal of the lubricating film between the first sealing lip and the shaft to be sealed by constant circulation of the lubricant.
  • the dynamically stressed first sealing lip can be assigned a protective sealing lip on the side facing away from the space to be sealed, which prevents the first sealing lip from being exposed to pollutant particles that reduce the service life.
  • the radial distance between the inner diameter of the first sealing lip and the pipe socket is 0.25 to 1 times as large as the axial extension of the stiffening ring the first Axial leg opposite side.
  • a small radial distance between the input shaft and the pipe socket requires a dimensionally stable design of the seal even when the input shaft is displaced in the axial direction, for example caused by thermal expansion.
  • the spatial assignment of the dynamically stressed first sealing lip does not change its position with respect to the surface of the shaft to be sealed, so that the sealing properties are always constant, for example a constant return flow effect during the intended use.
  • the guide sleeve according to the invention is explained in more detail below using an exemplary embodiment. This shows the individual components to be taken into account, partly in a schematic representation.
  • the guide sleeve 1 shows a guide sleeve 1 with an integrated seal 2, which is used in the area of the clutch release bearing of a transmission, for example for motor vehicles.
  • the guide sleeve 1 comprises a pipe socket 4, which surrounds an input shaft 3 of the transmission on the circumference at a radial distance.
  • the gear not shown here, is flanged to the guide sleeve 1 on the side 16 facing the medium to be sealed.
  • the pipe socket 4 and the mounting flange 5 are integrally formed into one another and consist in this embodiment a deep-drawn sheet.
  • the pipe socket 4 comprises a radially inner first axial leg 6 and a radially outer second axial leg 7, which are connected to one another via a radial leg 8.
  • the radially inner first axial leg 6 surrounds the stiffening ring 11 under radial prestress, the stiffening ring 11 touching the pipe socket 4 in the area of its axial and in the area of its radial extent.
  • the seal 2 is held by a frictional connection between the stiffening ring 11 and the first axial leg 6.
  • the seal 2 comprises a dynamically stressed first sealing lip 9 which dynamically seals the input shaft 3 to be sealed.
  • two statically stressed second sealing lips 10, 12 are arranged, which are associated with one another at a radial distance, the gap 13 formed by the radial distance between the second sealing lip 10 and the additional sealing lip 12 being filled with grease .
  • the manufacture of the claimed guide sleeve 1 is particularly simple, since it consists of only two parts to be fixed together.
  • the pipe socket 4 with the one-piece fastening flange 5 forms in the area of the first axial leg 6 the receptacle for the seal 2, in which the first sealing lip 9 and the second sealing lip 10 are fixed in one piece and merged onto a stiffening ring 11.
  • the ratio of the axial expansion to the radial expansion is 1: 1 to 1.0.25, preferably 1: 0.75 to 1: 0.5, an exact assignment which is always constant during the intended use is constant conditional between the individual parts of the guide sleeve 1.
  • the second axial leg 7 completely covers the statically stressed second sealing lip in this exemplary embodiment, so that mechanical damage to the second sealing lip 10 can be reliably avoided.
  • the second axial leg 7 is arranged such that it rests against the outer wall of the transmission at a predetermined elastic preload of the second sealing lip 10 and thereby an even greater deformation , possibly overstressing the second sealing lip 10, prevented.
  • the axial extent of the seal 2 is twice as large as the radial extent.
  • the pipe socket 4 of the guide sleeve 1 is shown as a single part, which is integrally formed with the mounting flange 5.
  • the mounting flange 5 has three evenly distributed recesses for attachment to the outer wall of the transmission housing.
  • the radially outer, second axial leg 7 of the pipe socket 4 completely covers the statically stressed second sealing lip 10 radially on the outside and thereby protects it from harmful mechanical influences.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Devices (AREA)
  • Fluid-Damping Devices (AREA)
EP92121544A 1992-07-22 1992-12-18 Führungshülse mit integrierter Dichtung für ein Kupplungsausrücklager eines Getriebes Expired - Lifetime EP0579869B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4224179A DE4224179C1 (de) 1992-07-22 1992-07-22 Führungshülse mit integrierter Dichtung für ein Kupplungsausrücklager eines Getriebes
DE4224179 1992-07-22

Publications (3)

Publication Number Publication Date
EP0579869A2 EP0579869A2 (de) 1994-01-26
EP0579869A3 EP0579869A3 (enrdf_load_stackoverflow) 1994-08-03
EP0579869B1 true EP0579869B1 (de) 1996-09-04

Family

ID=6463835

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92121544A Expired - Lifetime EP0579869B1 (de) 1992-07-22 1992-12-18 Führungshülse mit integrierter Dichtung für ein Kupplungsausrücklager eines Getriebes

Country Status (7)

Country Link
US (1) US5368397A (enrdf_load_stackoverflow)
EP (1) EP0579869B1 (enrdf_load_stackoverflow)
JP (1) JPH06185540A (enrdf_load_stackoverflow)
AT (1) ATE142315T1 (enrdf_load_stackoverflow)
BR (1) BR9302713A (enrdf_load_stackoverflow)
DE (2) DE4224179C1 (enrdf_load_stackoverflow)
ES (1) ES2092006T3 (enrdf_load_stackoverflow)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4327929A1 (de) * 1993-08-19 1995-02-23 Bruss Dichtungstechnik Abdichtung für die Führungshülse des Ausrücklagers einer Kupplung
US5498085A (en) * 1994-12-15 1996-03-12 Chrysler Corporation Shaft sealing systems
JP3305591B2 (ja) * 1996-09-26 2002-07-22 富士機工株式会社 ステアリングコラム用軸受
DE19711400C2 (de) * 1997-03-19 2001-12-06 Freudenberg Carl Fa Radialwellendichtring
US6177744B1 (en) * 1998-03-17 2001-01-23 Reliance Electric Technologies, Llc Seal arrangement for an electric motor
JP4957937B2 (ja) * 2001-07-27 2012-06-20 Ｎｏｋ株式会社 密封装置
US7419305B2 (en) * 2001-08-24 2008-09-02 Reliance Electric Technologies Llc Sealing system for bearing assembly
DE20321639U1 (de) 2003-06-03 2008-09-18 Carl Freudenberg Kg Montageschutzring
US7226212B2 (en) * 2004-03-01 2007-06-05 Minebea Co., Ltd. Shield and sealing method for a hydrodynamic bearing
US7461907B2 (en) * 2005-07-18 2008-12-09 Bendix Spicer Foundation Brake Llc Rod/seal bearing arrangement utilizing locking fingers
CN101563546B (zh) * 2006-12-06 2012-07-18 胡斯华纳有限公司 内燃机的曲轴轴承装置
FR2986598B1 (fr) * 2012-02-03 2015-03-27 Freudenberg Carl Kg Joint d'etancheite
FR3020421B1 (fr) * 2014-04-24 2016-12-30 Skf Ab Palier a roulement, notamment pour dispositif de butee de debrayage
CN106321846A (zh) * 2016-11-10 2017-01-11 昆山健博密封件科技有限公司 一种双骨架油封件
CN109882507B (zh) * 2017-12-06 2020-10-27 舍弗勒技术股份两合公司 用于双离合器变速器的轴承装置
EP4097368B1 (en) * 2020-01-30 2024-12-04 Ngi A/S Bearing house design

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1867721U (de) * 1962-12-20 1963-02-21 Elektro Motoren Feinbauwerk Gr Hutmanschetten-wellendichtung.
DE7509224U (de) * 1975-03-22 1975-07-17 Skf Kugellagerfabriken Gmbh Fuehrungshuelse
JPS57111683A (en) * 1980-12-27 1982-07-12 Fujitsu Ltd Document storage device
JPS5884513A (ja) * 1981-11-13 1983-05-20 Nippon Gakki Seizo Kk 利得制御増幅器
JPS61209121A (ja) * 1985-02-05 1986-09-17 Sanyo Kokusaku Pulp Co Ltd 金属層を含む熱可塑性樹脂シ−トの製造方法
FR2611833B1 (fr) * 1987-02-24 1989-06-30 Hutchinson Perfectionnements aux tubes-guides disposes entre la boite de vitesses et l'embrayage d'un vehicule et aux joints equipant de tels tubes-guides
FR2618864B1 (fr) * 1987-07-28 1991-06-21 Procal Tube-guide pour butee de debrayage de boite de vitesses de vehicule automobile
FR2629539B1 (fr) * 1988-04-05 1993-04-16 Procal Tube-guide a etancheite integree pour butee de debrayage de boite de vitesses de vehicule automobile
DE3816890A1 (de) * 1988-05-18 1989-11-30 Schaeffler Waelzlager Kg Ausruecklagereinrichtung fuer eine gedrueckte kraftfahrzeugkupplung
US4960193A (en) * 1989-01-27 1990-10-02 Ina Bearing Company, Inc. Concentric slave cylinder
FR2656395B1 (fr) * 1989-12-22 1994-12-30 Procal Tube-guide a etancheite integree pour butee de debrayage de boite de vitesses de vehicule automobile.
FR2682441B1 (fr) * 1991-10-15 1993-12-10 Procal Tube-guide a etancheite integree pour butee de debrayage de boite de vitesses de vehicule automobile.

Also Published As

Publication number Publication date
US5368397A (en) 1994-11-29
DE59207065D1 (de) 1996-10-10
BR9302713A (pt) 1994-02-01
DE4224179C1 (de) 1993-11-11
JPH06185540A (ja) 1994-07-05
EP0579869A3 (enrdf_load_stackoverflow) 1994-08-03
ES2092006T3 (es) 1996-11-16
ATE142315T1 (de) 1996-09-15
EP0579869A2 (de) 1994-01-26

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